200813316 九、發明說明： 【發明所屬之技術領域】 本案係2006年6月29日由Marion Brecheisen所提出申 請之美國第1 1 /47 8,202號專利申請案「自地下地層回收流 體之雙缸式揚升泵及方法」之部分接續案，且此美國前案 係以參考之方式被倂入本文中。 本發明係有關於井下抽吸系統，且尤有關於一種用於從 地下地層處抽取流體（諸如油及瓦斯）之低外形泵揚升機 系統及方法。 【先前技術】 多年來已發展出許多種類之抽吸裝置，以供從鑽入地下 地層內之井中抽取流體。一通常被稱爲「遊樑式泵」之習 知裝置的特徵在於具有一被繫接於此樑之一端部上之抽吸 桿串，而此樑係由一動力驅動源（諸如一藉由一連接桿臂 而被聯接至此樑之相對向端部上之馬達）所驅動。典型地， 抽吸桿將延伸至井內相當深之距離，並被連接至一井下 泵，且將因應透過連接桿臂之推動力所起動之重量而被上 升及下降，藉以導致流體從井內被汲出。 遊樑之搖擺運動將平衡被升起之流體的重量，且在當抽 吸桿係部分地由於抽吸桿串之重量、被升起之流體的重 量、及克服在抽吸桿下行衝程之荷重慣性所需要的力而開 始其上行衝程時，此重量將達到最大程度；而在5000呎至 6000呎等數量級之深井中，抽吸桿及被升起之油的重量可 能會超過8000磅。由於當泵桿穿過地層前進時爲克服流體 壓力所遭遇之阻力，以致一較小於或相等於此流體壓力之 200813316 荷重將在每一下行衝程期間被加至動力驅動源上。此遊樑 式泵揚升機之優點及缺點係爲習知且被詳細地記錄，因此 已有許多不同之方法已被利用，並已獲致不同程度之成 就。儘管如此，仍存在著對一種泵揚升機之需求，其係低 外形、可被安裝在地面上或下並具有一可調整長度衝程、 且低電力需求，及藉由這些來克服遊樑式泵中之桿速及衝 程控制的固有問題。 有必要進一步地使泵桿運行之上及下端部處之壓力驟升 現象減至最小，以便可避免應力集中在諸桿接頭上，否則 其可能導致桿之伸展、鬆弛及毀壞。 【發明內容】 在本發明之一重要特徵中，若干新穎且經改良之井口缸 一起運轉在泵桿或抽吸桿之諸相對側上；另外，由於缸之 效率及抽吸桿串之荷重或重量、被升起之流體的量、與荷 重在完成每一下行衝程後之慣性的平衝，使得諸缸中之每 一者均可藉由氮氣與其下方之液壓流體的組合或者單只藉 由氮氣而在實質較低之馬力需求下被平衡，而且可平衡在 每一上行衝程期間推進抽吸桿向前之諸力或者抵抗抽吸桿 向前之阻力。 根據本發明之另一特徵，位在泵桿之相對側上之諸平衡 缸被可調整地連接至一橫桿之諸相對端部上，以便可精準 地將泵桿定位在其間之中央處；且諸缸具有藉由調節流體 流向諸缸之流動壓力及方向而在一廣闊範圍中嚴密地控制 泵循環速率及泵桿衝程長度之能力。在將泵桿定位在諸缸 間之中央處的過程中’栗桿之衝程長度可被減小至足以使 200813316 泵桿可連續操作而不致妨礙到其他操作，諸如一般被稱爲 中心樞軸式及側向移動式之地面上機動灌溉系統，而此類 中心樞軸灌溉系統配備有若干噴灑器，此類側向移動灌溉 系統則具有一系列噴灑管，其可前後推進而涵蓋整個田地。 在其他特徵中，另還可提供一可被安裝在地面上或下方 之抽吸系統，其可在與傳統馬頭式泵揚升機相較只要極低 之馬力需求下而更具能源效率，以致可使用太陽能作爲其 電力來源，且其需較少之維護、重量輕、且相對於一般所 必要之全尺寸牽引式掛車，其可輕易地藉由小貨車而被來 ®地搬運於田地間，以致建造及安裝所需之升起裝置或起 重裝置減至最少，而具有增長使用壽命之最小數量活動部 件例如可由一電腦所遙控，而此電腦將同時控制多個泵揚 升機’其具有在數毫秒內調整泵抽吸速度以及諸缸與泵桿 之衝程長度的能力，此諸泵揚升機可經由網路或使用可程 式PC板之電話而被監視及控制，且諸PC板可保留訊息並 提供物主所需之針對諸如使用、生產、故障、電力使用、 泵抽吸體積、系統問題等事項之報告，以及可監控整個系 統之機能狀況，包括過濾器、油高度、泵抽吸活動力、電 源、運轉時間、及生產標準，且具有在必要時不需人力介 入之下使系統停機。 根據本發明之一觀點，一種用於使一泵桿串往復運動於 一油井或其他流體井中之泵揚升機包括··一接地基架；泵 桿串之一上端部，其向上延伸穿過基架；及若干活塞驅動 缸總成，其被安裝在基架上以便可延伸於泵桿串之諸相對 側上’其中壓力下之流體被選擇地引進諸缸總成內，以便 200813316 可逆地一同驅動諸活塞中之每一者，藉以使泵桿串作往復 運動。在另一觀點中，諸缸總成中之每一者包括用於平衝 泵桿串之荷重或重量之裝置，其包含被升起之流體的量與 荷重在完成每一下行衝程後之慣性，並且可平衡在每一上 行衝程期間抵抗抽吸桿串向前之阻力。 " 另一觀點係爲一種從地下地層處回收流體之方法，其中 - 一泵桿串向下延伸至該地層內，並包括下列之步驟：將一 對液壓流體缸總成安裝於此延伸於地面上之泵桿串的上端 r 部之諸相對側上；將壓力下之液壓流體施加至諸缸總成， 以便可使該泵桿串作往復運動；及平衡此泵桿串及從該地 下地層處被抽出之諸流體的重量，以便可在諸缸中的液壓 流體壓力與泵桿串的重量之間達成平衡。最合意地，平衡 係藉由利由一流體迴路而被達成，此迴路將壓力沿一向上 方向而施加在每一活塞之整個上端部，並對等地在每一上 行衝程時將壓力下之液壓流體施加至每一活塞之下端部， 且當壓力下之流體沿一向下方向作用在諸活塞時，同時將 , 流體壓力從諸活塞之上及下端部處釋放，以便可起始此泵 i. 桿串之下行衝程；且平衝流體迴路至少部分地係由一可壓 縮氣體（諸如單獨氮氣或者油上之氮氣）所組成。諸經平 衡之缸的運用會導致極低之馬力需求。例如，正常液壓缸 需要2500-3000psi，而諸經平衡之缸則需要小於正常需求 之1 0 %，且甚至可能小於2 5 0 p s i之液壓壓力。此亦導致可 使用較小缸且可容納任何所需升起高度之能力。 根據另一觀點並與前述之平衡缸配合協作的，一液壓控 制迴路包括：一方向控制閥；一控制開關，其被連接至方 200813316 向控制閥，以便可調整壓力下之液壓流體經由壓力及返回 管線之流動，藉以可逆地驅動諸驅動缸中之每一者；且其 特徵在於一壓力延遲缸，其內具有一活塞頭，及被連接至 諸壓力及返回管線中之每一者上之延遲缸的兩相對端部， 其中方向控制閥經由控制開關而達成之反轉，將使得壓力 下之流體在連續地經由諸壓力及返回管線中之每一者推進 以反轉驅動缸之衝程前，先連續地經由此延遲缸之諸相對 端部而塡滿此延遲缸。 除了上述之方法及設備之外，另外之觀點與實施例將經 由參照諸附圖及硏讀下列說明而變得顯而易知。若干例示 用實施例配合諸圖式而被說明。本文中所揭示之諸實施例 與諸圖式將被視爲例示說明用而非作爲限定。 【實施方式】 詳細參照諸圖式，藉由第1及2圖中之說明性範例而顯 示一用於從地下地層處抽取油及瓦斯之泵揚升機系統1 〇， 其槪括地包括一基架或平台1 2，其可藉由位於混凝土基座 1 6上之調整螺桿1 4而被裝設；且一習知之泵桿向下延伸穿 過一現有之井套管20，並在兩相對側上與諸缸總成22成側 面相接，而每一總成22具有一活塞24，其上端被安裝至一 橫桿26上。在第1至4圖所示之實施例中，一種液壓流體 與氮氣之組合可藉一種將於下文中描述之方式而從一連接 至貯槽3 2及氮氣供應源3 4上之液壓馬達3 0處被供應至各 缸22。一適當之控制面板36調整對諸缸22之液壓流體供 應，以便可經由被可調整地安裝在泵桿上端部上之橫桿2 6 及泵桿夾鉗3 8而控制泵桿之升起及降低。 -10 - 200813316 此泵桿總成係屬習知之結構，其具有一串延伸穿過井套 管之桿，並配備有一井下泵，其具有一可在此泵桿串之諸 交替衝程進行時強制流體向上通過套管。此泵桿串可向下 延伸達可觀之距離，而此諸距離延伸在從數百呎至數千呎 深之任何地方。因此，在此泵桿串之每一上升衝程時，諸 缸總成22必須能不只克服泵桿總成及其井下配件之重 量，還要能克服被升起至地面之流體的重量，以及其他慣 性力與摩擦力。此外，當泵桿總成被反轉以完成每一循環 時，諸缸22將會被強制去克服在每一下行衝程時較小或相 等之荷重。 第2圖更詳細地說明平台或基架1 2，其包括藉由若干相 隔且平行之橫向支架42而被連接在一起之若干相隔且平 行之I型樑40，而在四個隅角中之每一者處設有一混凝土 基座16，其各可被安裝在所要之深度處，以便可連同諸調 整螺桿1 4而一起補償地形上之傾斜或差異。將可輕易地察 知的是，基架1 2可被修改成可用於離岸平台作業。同等重 要地，基架12係被安裝在一現有之泵桿18及其套管20上， 且在地面上之作業中，必要之孔被鑽入地面之中以便可將 缸22插置入缸套筒護箍44內。本實施例之另一特徵在於 其可運用在許多田地中之能力，而在此諸田地處，其他之 地面上作業（諸如自動灌溉系統，其配備有若干遍及田地 極大面積之遊樑）正持續地運作著，且諸灌溉管線通常被 升高離地不超過8至1 0呎。爲使泵揚升機系統可持續運 轉，很重要的是可限制泵揚升機及諸缸2 2在地面上之衝程 長度，以便不妨礙諸灌溉管線之前進，且同時維持大體上 -11- 200813316 可持續回收諸如油、瓦斯或水等之地下地層流體。 上橫桿26係成一空心且槪略呈矩形之樑型式，其上經 若干連接板46而繫接活塞24之諸上端部。諸連接板46 焊接至活塞24之諸上端部，且各連接板46藉由若干U 螺栓或連接帶48而被可調整地繫接至橫桿26之底面。 連接帶48使得上活塞端部之諸連接板46可在橫桿26之 長上滑動地調整，直到泵桿1 8被精準地定位在諸活塞間 中央處。參照第3圖所示，必須留意的是各活塞24之上 部包括一具有上斜邊5 2之實心錐形頭部5 0，其可被插入 管狀收納件54內，而此收納件54具有一與頭部50之外 形壁表面成互補之內錐形壁56,且收納件54之上緣被焊 至連接板4 6，並使錐形頭部5 0被楔牢於收納件5 4內。 第4及5圖詳細說明分別位於升高及降低位置上之諸 塞總成24中之一者。各活塞總成24包括一具有被永久 繫接於上擴大端部50上之上螺紋端部6 1的長條狀活塞 60，且向下延伸穿過一較小直徑之活塞管62而終止於一 永久地繫接於活塞頭64上之下端部63中，此活塞頭64 收納與活塞管62之內壁成可滑動但密封啣合狀態之密 件66、66’及磨耗環68。活塞管62終止於一下螺紋端 72中，其被繋接至缸頭75之內壁74的上端部。缸頭 中之一中心孔收納一肘形配件76,其與第二配件77相連 於一延伸自接口 79處之液壓管78的下端部處。 液壓輸送管7 8向下延伸穿過位於外同心缸8 2與內同 之下方圓筒形延伸部84間的環域或外腔室80。此延伸 8 4從一位在外同心缸8 2之上端部處之校準環8 6起向下 由 被 形 諸 縱 之 端 錐 接 活 地 軸 被 則 封 部 75 結 心 部 延 -12- 200813316 伸，並具有一被繫接至缸頭7 5之外壁8 8上之下螺紋端部 87，而缸頭75相對於管件84具有增大之厚度，且與套筒 74係一體成型並成外間隔之同心關係。一系列緊密間隔之 孔63彼此成圓周間隔關係地垂直延伸穿過一位於套筒74 與外壁8 8間之缸頭7 5的中間部分，以便可分別地建立油 • 在內及外腔室92、80間之流動的連通。校準環86具有一 - 形成於弧形半徑上之外表面，其與一位於環形基座8 7上之 互補內表面相啣合地被楔牢，以便可在基座87上自行校 f 準，並可被裝設在該橫桿42之間，如第2圖中所示。在第 3圖中，爲清晰起見，校準導件86被顯示成與基座87成間 隔關係，但在實際操作中將會與元件8 7保持密封啣合之狀 態，如第4及5圖中所示。 一較大直徑之活塞管102具有一上內螺紋端部103,其被 * 永久地繫接於活塞軸60之上錐形頭部50上，此活塞管102 . 以可滑動但密封啣合之狀態向下地延伸穿過缸蓋1 00，而此 蓋100在其上端部處具有與外管102成密封接觸狀態之內 4 密封件104、104’ 。此管102向下地延續而終止於一與下 圓筒形延伸部84成密封但可滑動啣合狀態之套筒1 06中， 而此套筒106在上端部處具有一外肩部90，且若干油封 107、107’被插置在套筒端部106與圓筒形延伸部84之 間。一接口 108延伸穿過上端部96而與位於下圓筒形延伸 部84與活塞管102間之環狀流體通道109相連通，以便可 用一將於下文中描述之方式將活塞從第4圖所示之升高位 置驅動至第5圖所示之降低位置。 一接口 110被安置於校準環8中，以便可用一將於下文 -13- 200813316 中描述之方式將壓力下之氮氣引進環域80內，以便可平 泵桿串之重量。在此關係下，外缸82之下端部被一具有 放塞85之端板83所關閉。然而，位在諸管62及102之 端部處的缸頭7 5具有一*系列之孔6 3 ^以致使位於諸管 及102間之通道92可與環域80成敞開之流體連通狀態 環域80被塡充以液壓流體達一高度處，以便使得在此環 被預先從供應槽3 4處裝塡以惰性氣體（諸如壓力下之 氣）時可迫使液壓流體向上塡滿內腔室92，如第6圖中 示，而腔室92中之任何空氣均從位在活塞管102之上盡 末端處之排放孔101逃逸。槽34經由具有切斷閥122之 口管線1 2 3而被塡充以來自一適當來源（諸如一經加壓 氮氣瓶）處之氮氣。依次地，若干出口管線124從槽34 導入諸接口 1 1 0，以便如前述般地塡滿各環域8 0，且氮 壓力可藉由壓力調節器35而被調節，以便可在氣體G及 第4圖中所示之油F ’間建立所要的平衡。另一位於管 1 24中之閥1 22在泵桿已經平衡之後接著被關閉。很重要 必須留意的是，在抵銷或平衡泵桿1 8及如先前所述般地 地層處被升起之油或其他流體的重量期間，以F及F’ 代表之油係與被聯結於栗3 0及槽3 2上之液壓控制迴路 隔離狀態。 如第4至6圖中進一步說明的，液壓泵3 〇經由管線] 通過方向控制閥1 1 2及上升管線1 1 4，將壓力下之液壓流 供應至諸接口 79中之每一者及管78內，並向上進入位 套筒74中之內同心通道73內，以便作用在兩缸22中之 塞端部6 4的整個底面上。一位在管線1 1 1中之流量控制 衡 排 下 62 〇 域 氮 所 頭 入 之 處 氣 如 線 且 從 所 成 11 體 於 活 閥 -14- 200813316 1 1 6可被手動地控制或被遙控，以便在朝一通過各單獨活塞 管62之方向驅動各活塞軸60期間可調整被輸送至活塞端 部64之流體體積。在提升或抬升諸活塞24之過程中，橫 跨諸活塞端部64之流體壓力將藉由腔室92中之流體壓力 而被增大，以致使在腔室80中之流體高度將隨著其被壓力 下之氮氣強迫進入腔室92內而被降低。位於諸缸22中之 諸活塞24藉由前述之液壓控制迴路而被一起抬升，以便可 升起抽吸桿1 8 —段由方向控制閥1 1 2所決定之預定距離。 閥滑軸1 1 3如第6圖所示般地在一極限開關2 5之控制下被 移至左側，而此極限開關則如第1圖所示般地被定位在橫 桿25之運行路徑中。此極限開關在高度上可被調整，以便 可控制抽吸桿1 8之衝程長度。 藉由使經過方向控制閥1 1 2之流體的流動反向，壓力下 之液壓流體經由管線1 15而被導引至諸缸之接口 1〇8,以便 可經由位在外活塞管1 02與圓筒形延伸部84間之外通道 1 09而供應此壓力下之液壓流體，以便可作用在位於套筒上 端部處之整個外肩部90上，並將諸活塞中之每一者向下驅 動以使抽吸桿1 8之衝程反向。輸送管7 8中之壓力下的液 壓流體不受約束地經由管線1 1 4及下返回管線1 1 8而返回 至液壓貯槽3 2內。同時，諸活塞24之上端部將迫使在內 腔室92中之一些液壓流體返回至環域80,並將氮氣壓縮至 某種程度，以致使得液壓流體高度與其在如第4圖所示之 下行衝程開始時之高度相較係爲被升高的。因此’在如第 5圖所示之諸活塞24及抽吸桿1 8之下行衝程終了時’外環 域80中之氮氣及液壓流體將在上升衝程間始時恢復至與 -15- 200813316 抽吸桿之重量相平衡之平衡狀態下。一位於控制管線中之 壓力釋放閥1 20允許液壓流體在發生超載之情況下可經由 管線1 1 8而返回至槽3 2。 爲說明而非限定之目的，較深井所用之氮氣可在3 00psi 至3 5 0psi之數量級上；而較淺井所用者則大致上可被降 | 低。一旦泵桿1 8已經平衡，衝程速度可藉由透過流量控制 ' 閥72控制液壓流體之體積或質量流率而被設定，且衝程長 度可如先前所述地藉由極限開關25或一位於灌溉控制面 / 板上之適當遙控開關1 26而被調整。因此，在一圓形灌溉 系統中，遙控計時器開關1 26經由管線被連接至閥11 3，以 便可選擇地縮短泵桿之衝程，使其不致會妨礙到灌槪控制 管線在橫跨諸泵桿中之每一者期間之前進。此外，液壓流 體壓力可與衝程長度成比例地變變，以便可例如在當衝程 長度被減小時，液壓壓力可被增大，以便能增加衝程之速 度，且仍可從井中抽取出相同量之流體。 其他實施例之詳細說明 毫: 第7及8圖說明一用於泵揚升機之另一實施例的缸總成 22’ ，且其中相類似之部分被對應地以原有 > 元件符號標 示。事實上，缸總成22’相當於前一實施例中之缸總成22， 除了其利用氮氣作爲僅有之平衡流體，以取代前述在油上 方塡充氮氣作爲平衡流體者。雖然未示於圖，但諸缸總成 之液壓控制迴路以及氮氣供應槽均相同於第1至6圖所示 及所述者，除了液壓流體或油並未被引進環域80’或腔室 92’內之差異外。作爲取代的，氮氣被引進接口 1 1〇’ ，直 到其到達平衡泵桿串1 8之荷重所需之壓力標準爲止，此如 -16- 200813316 先前在第1至6圖中所述者。氮氣壓力標準可藉由供應槽 34上之壓力調節器而被適當地調節，以便使得一旦達到適 當之平衡後便將被關閉。因此，在第8圖所示之下行衝程 進行中，活塞頭50’將向下推進以迫使氮氣離開腔室92’ 並進入環域80’內，以便可略微增加環域80’中之氮氣壓 力。相反地，在第7圖所示之上行衝程進行中，氮氣將隨 著活塞頭50’之向上移動而塡滿流體通道92’ ，並略微地 減小氮氣壓力以備進行下一個下行衝程。 在其他優點中，還有在如第1至6圖中所示地在油F及 F’上方利用氮氣之優點在於：那些被暴露在油F而非氣體 G中之密封件將不易受到洩漏之影響，且任何在活塞端部 64與管62間之磨耗表面均被潤滑，因而可在田地中具有較 長之耐用壽命。 在第9至11圖中所示之實施例中，第6圖所示之液壓控 制迴路被修改成可包括一延遲缸1 3 0，其被安裝在諸控制管 線1 1 4及1 1 5之間，以便可調節流體壓力且尤其可減緩在 每一上行及下行衝程開始時之流體壓力驟升及加速衝擊。 相類似之部分被對應地以第6圖中之元件符號標示，且此 延遲缸係由在各端部處均被一端板1 34所關閉之外圓筒形 管132所構成，此端板134藉由若干緊固件135而被繫接 至一密封板1 3 6上，而此密封板1 3 6被嵌入管1 3 2之端部 內且配備有一與管132之內壁相啣合之〇形環137。雖然 未示於圖，諸端板1 3 4可被牢固地夾持在管1 3 2之兩相對 端部上，以便可將諸密封板1 3 6固定在管1 3 2之兩相對端 部處的適當位置上。一位於缸1 3 0之各端板1 3 4中的油接 -17- 200813316 口 138藉由一流體管線140而被連接至諸流體管線114及 115中之一者上，且一位在各端部處之空氣排放口 142可藉 手動方式打開，以便在第6圖之控制迴路運作之前先將空 氣自缸130中排除。一位於缸中之浮式缸頭144上配備有 若若油封146與若干磨耗環148之組合，以便可在活塞頭 ' 144之外表面與缸130之內壁表面間建立可滑動但密封之 • 啣合。 如前所述者，泵3 0導引液壓流體通過管線1 1 1及方向控 ， 制閥1 1 2經由管線1 1 4而進入諸接口 79中之每一者內，以 ~+便可將諸缸22 —起提升並舉起抽吸桿18,或可藉由移動方 向閥1 1 2而使流動反向，以便可導引流體通過管線1 1 5而 到達諸接口 1 0 8，藉而使抽吸桿1 8之衝程反向；且在輸送 管7 8中之液壓流體不受約束地經由管線1 1 4而返回至貯槽 32。相反地，當流體在上升衝程進行期間被導引通過管線 1 1 4時，流體將經由管線1 1 5而返回至貯槽3 2。 爲了在每一上行衝程及下行衝程開始時防止壓力驟升及 , 加速衝擊，液壓流體起初將遵循最小阻力之路徑而進入延 遲缸130，藉此可迫使活塞頭144移至缸之一端部，如第 1 0圖中所示，且延遲或緩衝經分傳至將於井下被輸送之流 體的衝擊。每次控制迴路反轉其衝程時，如第1 1圖所示， 被強制進入缸1 3 0中之壓力下的流體亦將在作用抵擋殘留 在活塞頭之相對側中之流體的過程中多多少少被減少；而 在此相對側中之流體當然將不受約束地返回至貯槽3 2。一 旦活塞頭1 44被迫抵住缸1 30之各端部，則流體壓力將逐 漸地在壓力管線1 1 4或1 1 5中增升，且根據情況而作用至 -18 - 200813316 諸接口 79或108，並以對此井下串產生最小伸展或 情形反轉抽吸桿1 8之衝程。 如第9圖所示，第6圖中之泵系統被進一步修改 氮氣供應槽3 4，並作爲取代地直接經由閥而裝塡諸 例如，此經修改之系統具有特別適用於淺井之實同 ' 並不需要太大之壓力來平衡泵桿1 8以及從地層處 - 之油及其他液體的重量。可取代該槽3 4與其配件的 室80’被擴大至可達到儲存所要氮氣體積量所需之 Γ' 且當液壓流體被強制進入諸腔室80時將壓縮氮氣 一衝程之用。 由前述內容可察覺到，延遲缸130係適於與第1 中所示之系統以及剛剛敘述之第9至1 1圖中所示之 合使用。此外，諸未設有供應槽34之擴大腔室80’ 用於如第1至6圖中所示設有或未設有壓力延遲缸 系統中。 因此，應理解的是，雖然本文中提出並描述了多 例或觀點，但這些及其他修改型式均可在不脫離如 i . 請專利範圍所界定之本發明以及其合理均等物的精 圍下被達成。 【圖式簡單說明】 第1圖係可在地下地層中操作一泵桿串之泵揚升 施例之示意圖； 第2圖係第1圖中所示栗揚升機系統之略微分解： 第3圖係諸缸總成中之一者的更詳細縱向剖面圖 第3 A圖係第3圖中所示缸頭之詳細端面圖； 衝擊之 以去掉 缸22。 性，其 被升起 ，諸腔 程序； 以備下 至8圖 系統配 可被利 130之 個實施 後附申 神及範 機的實 ε體圖； -19- 200813316 第4圖係第3圖中所不缸總成之主要構成部分的另一*縱 向剖面圖，而此缸總成正處於完成上行衝程之狀態或位於 已升高之位置； 第5圖係第3及4圖中所示缸總成之另一縱向剖面圖， 而此缸總成正處於完成其下行衝程之狀態； 第6圖係第1及2圖中所示泵揚升機系統之示意圖，其 顯示液壓控制迴路以及用於平衡諸缸之氣體供應； 第7圖係一僅用氮氣作爲平衡流體之缸總成的另一實施 例之縱向剖面圖，而此缸總成被顯示正位於已升高之位置； 第8圖係第7圖所示缸總成之縱向剖面圖，而此缸總成 被顯示正處於完成其下行衝程之狀態； 第9圖係第1及2圖中所示泵揚升機系統之示意圖，而 此泵揚升機系統配備有一修正型式之液壓迴路及氮氣源； 第1 0圖係第9圖中所示液壓迴路用之延遲缸的詳細縱向 剖面圖，而此延遲缸配備有一活塞頭，其正處於一上升衝 程之開始並位在一移動盡頭末端處；及 第1 1圖係第1 0圖中所示延遲缸之縱向剖面圖，而此延 遲缸正處於一下降衝程之開始並位在相對向之移動盡頭末 端處。 【主要元件符號說明】 10 栗揚升機系統 12 基架/平台 14 調整螺桿 16 混凝土基座 18 栗桿/抽吸桿 -20- 200813316 18 泵桿串/抽吸桿串 20 套管 22 缸總成 22’ 缸總成 24 活塞 25 極限開關 26 橫桿 30 液壓馬達/泵 32 貯槽 34 氮氣供應源/供應槽 36 控制面板 38 泵桿夾銷 40 I型樑 42 橫向支架 44 缸套筒護箍 46 連接板 48 U形螺栓/連接帶 50 錐形頭部 50’ 活塞頭 52 上斜邊 54 管狀收納件 56 內錐形壁 60 活塞軸 61 上螺紋端部 62 活塞管 -21 - 200813316 63 下 64 活 66 密 66， 密 68 磨 72 下 73 內 74 內 75 缸 76 肘 77 第 78 液 79 接 80 80， rm 82 外 83 端 84 圓 85 排 86 校 87 下 88 外 90 外 92 內 92, 腔 端部/孔 塞頭/活塞端部 封件 封件 耗環 螺紋端部 同心通道 壁/套筒 頭 形配件 二配件 壓管 □ 域/外腔室 域 同心缸 板 筒形延伸部 放塞 準環 螺紋端部/環形基座 壁 肩部 腔室/通道 室/流體通道 -22- 200813316 96 上 λ山 m 部 100 缸 蓋 101 排 放 孔 102 活 塞 管 103 上 內 螺 紋 丄山 m 部 104 內 密 封 件 104’ 內 密 封 件 106 套 筒 107 油 封 107’ 油 封 108 接 □ 109 I祖 3¾ 狀 流 體 通 道 110 接 □ 110’ 接 □ 111 管 線 1 12 方 向 控 制 閥 1 13 閥 滑 軸 /閥 1 14 上 升 管 線 115 管 線 116 流 量 控 制 閥 118 下 返 回 管 線 120 壓 力 釋 放 閥 122 切 斷 閥 123 入 □ 管 線 124 出 □ 管 線 -23- 200813316 / 126 遙控開關 130 延遲缸 132 外圓筒形管 134 端板 135 緊固件 136 密封板 137 ◦形環 142 空氣排放口 144 活塞頭 146 油封 148 磨耗環 G 氣體 F, 油 F 油 -24-200813316 IX. INSTRUCTIONS: [Technical field to which the invention pertains] This application is the US Patent Application No. 1 1 /47 8,202 filed by Marion Brecheisen on June 29, 2006, "The double cylinder type of fluid recovered from the underground formation. Part of the continuation of the pump and method, and this prior US case is incorporated herein by reference. This invention relates to downhole suction systems, and more particularly to a low profile pump lift system and method for extracting fluids (such as oil and gas) from a subterranean formation. [Prior Art] Many types of suction devices have been developed over the years for extracting fluid from wells drilled into subterranean formations. A conventional device, commonly referred to as a "beam pump", is characterized by having a string of suction rods attached to one end of the beam, the beam being driven by a source of power (such as by A connecting rod arm is driven by a motor coupled to the opposite end of the beam. Typically, the suction rod will extend to a considerable depth within the well and be connected to a downhole pump and will be raised and lowered in response to the weight initiated by the urging force of the connecting rod arm, thereby causing fluid to flow from the well Was thrown out. The rocking motion of the beam will balance the weight of the fluid being lifted, and when the suction rod is partially due to the weight of the suction rod string, the weight of the fluid being lifted, and the load on the down stroke of the suction rod This weight will be maximized when the force required for inertia begins its upstroke; in deep wells of the order of 5000 呎 to 6000 ,, the suction rod and the raised oil may weigh more than 8,000 pounds. Because of the resistance encountered to overcome fluid pressure as the pump rod advances through the formation, a 200813316 load that is less than or equal to this fluid pressure will be applied to the power drive source during each downstroke. The advantages and disadvantages of this beam pump lift are well known and documented in detail, so many different methods have been utilized and have achieved varying degrees of success. Despite this, there is still a need for a pump lift that is low profile, can be mounted on the ground or below and has an adjustable length stroke, and low power requirements, and with these to overcome the beam type The inherent problems of rod speed and stroke control in the pump. It is necessary to further minimize the pressure swell at the upper and lower ends of the pump rod so as to avoid stress concentration on the rod joints, which may cause the rod to stretch, slack and destroy. SUMMARY OF THE INVENTION In an important feature of the invention, several novel and improved wellhead cylinders are operated together on opposite sides of a pump rod or a suction rod; in addition, due to the efficiency of the cylinder and the load of the suction rod string or The weight, the amount of fluid being lifted, and the flush of the inertia of the load after completion of each downstroke, such that each of the cylinders can be combined with nitrogen and the hydraulic fluid beneath it or by a single Nitrogen is balanced at substantially lower horsepower requirements and balances the forces pushing the suction rod forward or against the suction rod forward during each upstroke. According to another feature of the invention, the balance cylinders located on opposite sides of the pump rod are adjustably coupled to opposite ends of a crossbar so that the pump rod can be accurately positioned centrally therebetween; And the cylinders have the ability to tightly control the pump cycle rate and stroke length of the pump rod over a wide range by adjusting the flow pressure and direction of fluid flow to the cylinders. During the positioning of the pump rod at the center of the cylinders, the stroke length of the chestnut can be reduced enough to allow the 200813316 pump rod to operate continuously without hindering other operations, such as what is commonly referred to as a central pivot And laterally mobile on-ground motorized irrigation systems, such central pivot irrigation systems are equipped with a number of sprinklers, and such laterally moving irrigation systems have a series of spray tubes that can be advanced back and forth to cover the entire field. Among other features, a suction system that can be mounted on or below the ground can be provided, which is more energy efficient than a conventional horsehead pump lift with a very low horsepower requirement. Solar energy can be used as its power source, and it requires less maintenance, light weight, and is generally required to be carried by the small trucks in the field. Therefore, the lifting device or lifting device required for construction and installation is minimized, and the minimum number of moving parts having an increased service life can be remotely controlled by a computer, for example, and the computer will simultaneously control a plurality of pump lifts. Having the ability to adjust the pump suction speed and the stroke length of the cylinders and the pump rod within a few milliseconds, the pump lifts can be monitored and controlled via a network or a telephone using a programmable PC board, and the PC boards Retains messages and provides reports on what the owner needs for things like use, production, failure, power usage, pumping volume, system issues, etc., as well as monitoring the overall system's performance. This includes filters, oil level, pump suction activity, power, run time, and production standards, and has the system shut down without human intervention when necessary. According to one aspect of the invention, a pump lift for reciprocating a pump rod string in an oil well or other fluid well includes a grounding base; an upper end of the pump rod string extending upwardly therethrough a base frame; and a plurality of piston drive cylinder assemblies mounted on the base frame so as to extend over opposite sides of the pump rod string' wherein fluid under pressure is selectively introduced into the cylinder assemblies for reversible use of 200813316 Each of the pistons is driven together to reciprocate the pump rod string. In another aspect, each of the cylinder assemblies includes means for tapping the load or weight of the pump rod string, including the amount of fluid being raised and the inertia of the load after each downstroke is completed. And can balance the resistance against the forward stroke of the suction rod string during each upstroke. " Another point of view is a method of recovering fluid from a subterranean formation, wherein - a pump rod string extends down into the formation and includes the steps of: installing a pair of hydraulic fluid cylinder assemblies therewith On the opposite sides of the upper end r of the pump rod string on the ground; applying hydraulic fluid under pressure to the cylinder assemblies to reciprocate the pump rod string; and balancing the pump rod string from the underground The weight of the fluid being withdrawn at the formation to balance the hydraulic fluid pressure in the cylinders with the weight of the pump rod string. Most desirably, the balance is achieved by a fluid circuit that applies pressure to the entire upper end of each piston in an upward direction and equalizes the hydraulic pressure under each upstroke. Fluid is applied to the lower end of each piston, and when the fluid under pressure acts on the pistons in a downward direction, the fluid pressure is simultaneously released from above and below the pistons so that the pump can be started. The stroke is below the stroke; and the flushing fluid circuit is at least partially comprised of a compressible gas such as nitrogen alone or nitrogen on the oil. The use of the cylinders of the balances will result in extremely low horsepower requirements. For example, a normal hydraulic cylinder requires 2500-3000 psi, while a balanced cylinder requires less than 10% of normal demand, and may even be less than 250 psi. This also results in the ability to use smaller cylinders and accommodate any desired lift height. According to another aspect and in cooperation with the aforementioned balance cylinder, a hydraulic control circuit includes: a directional control valve; a control switch coupled to the side control valve of 200813316, so that the hydraulic fluid under pressure can be adjusted via pressure and Returning to the flow of the line, thereby reversibly driving each of the drive cylinders; and characterized by a pressure delay cylinder having a piston head therein and being coupled to each of the pressure and return lines Delaying the opposite ends of the cylinder, wherein the directional control valve is reversed via the control switch, such that the fluid under pressure is continuously advanced through each of the pressure and return lines to reverse the stroke of the drive cylinder The retarder cylinder is first filled continuously through the opposite ends of the retard cylinder. In addition to the above-described methods and apparatus, additional aspects and embodiments will become apparent from the accompanying drawings. A number of examples are illustrated with the embodiments in conjunction with the drawings. The embodiments and the figures disclosed herein are to be considered as illustrative rather than limiting. [Embodiment] Referring to the drawings in detail, a pump lift system 1 for extracting oil and gas from a subterranean formation is shown by the illustrative examples in FIGS. 1 and 2, which includes a A base frame or platform 12, which can be mounted by an adjustment screw 14 located on a concrete base 16; and a conventional pump rod extends downwardly through an existing well casing 20 and in two The opposite sides are joined to the side of the cylinder assembly 22, and each assembly 22 has a piston 24 whose upper end is mounted to a crossbar 26. In the embodiment shown in Figures 1 through 4, a combination of hydraulic fluid and nitrogen may be coupled from a hydraulic motor 3 0 to a sump 3 2 and a nitrogen supply 3 4 in a manner to be described hereinafter. It is supplied to each cylinder 22. A suitable control panel 36 adjusts the supply of hydraulic fluid to the cylinders 22 to control the rise of the pump rod via the crossbars 26 and the pump rod clamps 38 that are adjustably mounted on the upper end of the pump rod and reduce. -10 - 200813316 This pump rod assembly is a conventional structure having a series of rods extending through a well casing and equipped with a downhole pump having a force that can be forced during alternating strokes of the pump rod string The fluid passes upward through the casing. This pump rod string can extend down to a considerable distance, extending anywhere from hundreds of miles to thousands of feet deep. Therefore, at each rising stroke of the pump rod string, the cylinder assemblies 22 must be able to overcome not only the weight of the pump rod assembly and its downhole fittings, but also the weight of the fluid being raised to the surface, and other Inertial force and friction. In addition, when the pump rod assembly is reversed to complete each cycle, the cylinders 22 will be forced to overcome the smaller or equivalent load at each downstroke. Figure 2 illustrates the platform or pedestal 12 in more detail, comprising a plurality of spaced apart and parallel I-beams 40 joined together by a plurality of spaced and parallel transverse supports 42 and in four corners Each of them is provided with a concrete base 16, each of which can be mounted at a desired depth so as to compensate for the inclination or difference in the terrain together with the adjustment screws 14. It will be readily appreciated that the pedestal 12 can be modified to work on offshore platforms. Equally important, the pedestal 12 is mounted on a conventional pump rod 18 and its casing 20, and in the operation on the ground, the necessary holes are drilled into the ground so that the cylinder 22 can be inserted into the cylinder. Inside the sleeve guard 44. Another feature of this embodiment is its ability to be used in many fields where other ground operations (such as automatic irrigation systems equipped with a number of beams over a large area of the field) are continuing The ground is operating, and the irrigation lines are usually raised no more than 8 to 10 离 from the ground. In order for the pump lift system to operate continuously, it is important to limit the stroke length of the pump lift and the cylinders 2 2 on the ground so as not to impede the irrigation lines from entering, while maintaining a substantially -11- 200813316 Sustainable recovery of subterranean formation fluids such as oil, gas or water. The upper crossbar 26 is formed into a hollow, slightly rectangular beam pattern that is coupled to the upper ends of the pistons 24 via a plurality of webs 46. The webs 46 are welded to the upper ends of the pistons 24, and the webs 46 are adjustably attached to the bottom surface of the crossbar 26 by a plurality of U-bolts or straps 48. The connecting strip 48 allows the webs 46 of the upper piston end to be slidably adjusted over the length of the crossbar 26 until the pump rod 18 is accurately positioned at the center between the pistons. Referring to Fig. 3, it must be noted that the upper portion of each piston 24 includes a solid tapered head portion 50 having an upper beveled edge 52, which can be inserted into the tubular receiving member 54, and the receiving member 54 has a The inner tapered wall 56 is complementary to the outer wall surface of the head 50, and the upper edge of the receiving member 54 is welded to the connecting plate 4 6, and the tapered head 50 is wedged in the receiving member 54. Figures 4 and 5 detail one of the plug assemblies 24 located in the raised and lowered positions, respectively. Each piston assembly 24 includes an elongated piston 60 having a threaded end 61 that is permanently attached to the upper enlarged end 50 and extends downwardly through a smaller diameter piston tube 62 to terminate at A permanent attachment to the lower end portion 63 of the piston head 64 accommodates a tight member 66, 66' and a wear ring 68 that are slidable but sealingly engaged with the inner wall of the piston tube 62. The piston tube 62 terminates in a lower threaded end 72 that is coupled to the upper end of the inner wall 74 of the cylinder head 75. One of the center holes of the cylinder head houses an elbow fitting 76 which is coupled to the second fitting 77 at a lower end portion of the hydraulic pipe 78 extending from the port 79. The hydraulic delivery tube 78 extends downwardly through a ring or outer chamber 80 between the outer concentric cylinder 8 2 and the inner cylindrical extension 84 therein. The extension 8 4 extends from a calibration ring 86 at the upper end of the outer concentric cylinder 8 2 downwardly from the longitudinal end of the tapered end to the shaft, and the concentric portion of the sealing portion 75 extends -12-200813316. And having a threaded end 87 that is attached to the outer wall 8 8 of the cylinder head 75, and the cylinder head 75 has an increased thickness relative to the tubular member 84 and is integrally formed with the sleeve 74 and spaced apart Concentric relationship. A series of closely spaced apertures 63 extend vertically in a circumferentially spaced relationship through an intermediate portion of the cylinder head 75 between the sleeve 74 and the outer wall 8 8 so that oil can be separately established. • Inner and outer chambers 92 The flow of 80 flows. The calibration ring 86 has a surface formed on the outer radius of the arcuate radius that is wedged against a complementary inner surface on the annular base 87 so as to be self-aligning on the base 87. It can be installed between the cross bars 42 as shown in Fig. 2. In Fig. 3, for the sake of clarity, the alignment guide 86 is shown in spaced relationship with the base 87, but will remain in a sealed engagement with the component 87 in actual operation, as shown in Figs. 4 and 5. Shown in . A larger diameter piston tube 102 has an upper internally threaded end portion 103 that is* permanently attached to the conical head portion 50 above the piston shaft 60. The piston tube 102 is slidable but sealingly engaged. The state extends downwardly through the cylinder head 100, and the cover 100 has its inner seals 104, 104' at its upper end in sealing contact with the outer tube 102. The tube 102 continues downwardly and terminates in a sleeve 106 that is sealed to the lower cylindrical extension 84 but slidably engaged, and the sleeve 106 has an outer shoulder 90 at the upper end, and A plurality of oil seals 107, 107' are interposed between the sleeve end 106 and the cylindrical extension 84. An interface 108 extends through the upper end 96 to communicate with the annular fluid passage 109 between the lower cylindrical extension 84 and the piston tube 102 so that the piston can be removed from Figure 4 in a manner that will be described hereinafter. The elevated position shown is driven to the lowered position shown in FIG. An interface 110 is disposed in the calibration ring 8 so that nitrogen under pressure can be introduced into the ring region 80 in a manner as described in the following -13-200813316, so that the weight of the pump rod string can be equalized. In this relationship, the lower end of the outer cylinder 82 is closed by an end plate 83 having a plug 85. However, the cylinder heads 7 5 located at the ends of the tubes 62 and 102 have a * series of holes 63 3 such that the passages 92 between the tubes and 102 are open to fluid communication with the ring region 80. The field 80 is filled with hydraulic fluid to a level such that the fluid can be forced to fill the inner chamber 92 when the ring is pre-loaded from the supply tank 34 with an inert gas, such as a gas under pressure. As shown in Fig. 6, any air in the chamber 92 escapes from the discharge opening 101 at the end of the piston tube 102. The tank 34 is filled with nitrogen from a suitable source, such as a pressurized nitrogen cylinder, via line 1 2 3 having a shut-off valve 122. In turn, a plurality of outlet lines 124 are introduced from the slots 34 into the ports 110 to fully fill the ring domains 80 as described above, and the nitrogen pressure can be adjusted by the pressure regulator 35 so that the gas G and The desired balance is established between the oils F' shown in Figure 4. Another valve 1 22 located in the tube 1 24 is then closed after the pump rod has been balanced. It is important to note that during the offset or balancing of the weight of the pump rod 18 and the oil or other fluid that is raised at the formation as previously described, the oil system represented by F and F' is coupled to The hydraulic control circuit isolation state on the chestnut 3 0 and the slot 3 2 . As further illustrated in Figures 4 through 6, the hydraulic pump 3 供应 supplies the hydraulic flow under pressure to each of the ports 79 via the directional control valve 1 1 2 and the rise line 1 1 4 via the line] 78, and upwardly into the inner concentric passage 73 in the position sleeve 74 so as to act on the entire bottom surface of the plug end portion 64 of the two cylinders 22. One of the flow control balances in line 1 1 1 is the bottom of the 62-zone nitrogen. The gas is as straight as the line and can be manually controlled or remotely controlled from the valve to the valve-14-200813316 1 1 6 In order to adjust the volume of fluid delivered to the piston end 64 during actuation of each piston shaft 60 in a direction through each individual piston tube 62. During lifting or lifting of the pistons 24, the fluid pressure across the piston ends 64 will be increased by the fluid pressure in the chamber 92 such that the fluid level in the chamber 80 will follow The nitrogen under pressure is forced into the chamber 92 to be lowered. The pistons 24 located in the cylinders 22 are lifted together by the aforementioned hydraulic control circuit so that the suction rods 18 can be raised by a predetermined distance determined by the directional control valves 112. The valve slide shaft 1 1 3 is moved to the left side under the control of a limit switch 25 as shown in Fig. 6, and the limit switch is positioned at the running path of the cross bar 25 as shown in Fig. 1. in. This limit switch can be adjusted in height so that the stroke length of the suction rod 18 can be controlled. By reversing the flow of the fluid passing through the directional control valve 112, the hydraulic fluid under pressure is directed via line 115 to the ports 1B of the cylinders so that the outer piston tube 102 and the circle can be positioned The outer passages of the cylindrical extensions 84 are supplied with hydraulic fluid at this pressure so as to act on the entire outer shoulder 90 at the upper end of the sleeve and drive each of the pistons downward. In order to reverse the stroke of the suction rod 18. The hydraulic fluid under the pressure in the delivery pipe 78 is returned to the hydraulic sump 3 2 via the line 1 14 and the lower return line 1 18 without restriction. At the same time, the upper ends of the pistons 24 will force some of the hydraulic fluid in the inner chamber 92 back to the annulus 80 and compress the nitrogen to some extent such that the hydraulic fluid height is below its level as shown in FIG. The height at the beginning of the stroke is increased compared to the height. Therefore, 'at the end of the stroke of the piston 24 and the suction rod 18 as shown in Fig. 5, the nitrogen and hydraulic fluid in the outer ring region 80 will return to -15-200813316 at the beginning of the rising stroke. The balance of the weight of the suction rod is balanced. A pressure relief valve 120 in the control line allows the hydraulic fluid to return to the tank 32 via line 1 18 in the event of an overload. For purposes of illustration and not limitation, nitrogen used in deeper wells may be on the order of 300 psi to 350 psi; while those used in shallow wells may be substantially lowered. Once the pump rod 18 has been balanced, the stroke speed can be set by controlling the volume or mass flow rate of the hydraulic fluid through the flow control 'valve 72, and the stroke length can be set by the limit switch 25 or one as previously described. The appropriate remote control switch 1 26 on the control panel/board is adjusted. Thus, in a circular irrigation system, the remote timer switch 126 is connected to the valve 113 via a line to selectively shorten the stroke of the pump rod so that it does not interfere with the irrigation control line across the pumps Each of the rods comes before the period. Furthermore, the hydraulic fluid pressure can be varied in proportion to the stroke length so that, for example, when the stroke length is reduced, the hydraulic pressure can be increased to increase the stroke speed and still extract the same amount from the well. fluid. DETAILED DESCRIPTION OF OTHER EMBODIMENT: Figures 7 and 8 illustrate a cylinder assembly 22' for another embodiment of a pump lift, and wherein similar portions are correspondingly labeled with the original > component symbol . In fact, the cylinder assembly 22' is equivalent to the cylinder assembly 22 of the previous embodiment except that it utilizes nitrogen as the only equilibrium fluid to replace the aforementioned above-described gas filling with nitrogen as the equilibrium fluid. Although not shown in the drawings, the hydraulic control circuit and the nitrogen supply tank of the cylinder assemblies are identical to those shown and described in Figures 1 through 6, except that hydraulic fluid or oil is not introduced into the ring 80' or chamber. The difference within 92'. Alternatively, nitrogen is introduced into the interface 1 1〇' until it reaches the pressure standard required to balance the load of the pump rod string 18, as previously described in Figures 16 through 200813316. The nitrogen pressure standard can be suitably adjusted by the pressure regulator on the supply tank 34 so that it will be closed once the proper balance is reached. Therefore, in the course of the line stroke shown in Fig. 8, the piston head 50' will be pushed downward to force the nitrogen gas out of the chamber 92' and into the ring region 80' so that the nitrogen pressure in the ring region 80' can be slightly increased. . Conversely, during the upstroke shown in Figure 7, nitrogen will fill the fluid passage 92' as the piston head 50' moves upwardly and slightly reduce the nitrogen pressure for the next downstroke. Among other advantages, there is also the advantage of utilizing nitrogen over the oils F and F' as shown in Figures 1 through 6 that those seals that are exposed to the oil F rather than the gas G will be less susceptible to leakage. The effect, and any wear surface between the piston end 64 and the tube 62, is lubricated and thus has a long life in the field. In the embodiment shown in Figures 9 through 11, the hydraulic control circuit shown in Figure 6 is modified to include a retardation cylinder 130 which is mounted in control lines 1 1 4 and 1 1 5 In order to adjust the fluid pressure and in particular to slow down the fluid pressure swell and accelerate the impact at the beginning of each up and down stroke. The similar parts are correspondingly denoted by the reference numerals in Fig. 6, and the retardation cylinder is constituted by a cylindrical tube 132 which is closed by the one end plate 134 at each end, and the end plate 134 It is attached to a sealing plate 136 by a plurality of fasteners 135 which are embedded in the end of the tube 133 and are provided with a dome shaped to engage the inner wall of the tube 132. Ring 137. Although not shown, the end plates 134 can be securely held on opposite ends of the tube 132, so that the sealing plates 136 can be secured to opposite ends of the tube 132. In the proper position. An oil connection -17-200813316 port 138 in each of the end plates 134 of the cylinder 130 is connected to one of the fluid lines 114 and 115 by a fluid line 140, and one at each The air vent 142 at the end can be opened manually to exclude air from the cylinder 130 prior to operation of the control loop of Figure 6. A floating cylinder head 144 located in the cylinder is provided with a combination of an oil seal 146 and a plurality of wear rings 148 to establish a slidable but sealed seal between the outer surface of the piston head '144 and the inner wall surface of the cylinder 130. Cohesion. As described above, the pump 30 directs the hydraulic fluid through the line 1 1 1 and the direction control, and the valve 1 1 2 enters each of the interfaces 79 via the line 1 1 4, and can be replaced by ~+ The cylinders 22 lift and lift the suction rod 18, or the flow can be reversed by moving the directional valve 1 1 2 so that the fluid can be directed through the line 1 15 to the ports 1 0 8 . The stroke of the suction rod 18 is reversed; and the hydraulic fluid in the delivery tube 78 is returned to the sump 32 via the line 1 14 without restriction. Conversely, when the fluid is directed through line 1 14 during the ascending stroke, the fluid will return to sump 3 2 via line 115. In order to prevent pressure swells and accelerate the shock at the beginning of each upstroke and downstroke, the hydraulic fluid will initially enter the retardation cylinder 130 following the path of least resistance, thereby forcing the piston head 144 to move to one end of the cylinder, such as The graph is shown in Figure 10, and the delay or buffer is split to the impact of the fluid that will be transported downhole. Each time the control loop reverses its stroke, as shown in Figure 11, the fluid forced into the pressure in the cylinder 130 will also be in the process of resisting the fluid remaining in the opposite side of the piston head. How much less is reduced; and the fluid in this opposite side will of course return unrestricted to the sump 32. Once the piston heads 1 44 are forced against the ends of the cylinders 130, the fluid pressure will gradually increase in the pressure line 1 14 or 1 15 and, depending on the situation, act on the interfaces -18 - 200813316 Or 108, and reverse the stroke of the suction rod 18 with a minimum stretch or situation for the downhole string. As shown in Fig. 9, the pump system of Fig. 6 is further modified by the nitrogen supply tank 34 and, as an alternative, directly mounted via a valve, for example, the modified system has a particular application for shallow wells. It does not require too much pressure to balance the weight of the pump rod 18 and the oil and other liquids from the formation. The chamber 80', which can replace the tank 34 and its fittings, is enlarged to the point required to store the desired volume of nitrogen and will compress the nitrogen for one stroke when hydraulic fluid is forced into the chambers 80. It will be appreciated from the foregoing that the retarding cylinder 130 is adapted for use with the system shown in Figure 1 and as shown in Figures 9 through 1 1 just described. Further, the enlarged chambers 80', which are not provided with the supply grooves 34, are used in the system with or without the pressure delay cylinder as shown in Figs. Therefore, it should be understood that, although a plurality of examples or aspects are set forth and described herein, these and other modifications can be made without departing from the scope of the invention as defined by the appended claims. Was reached. [Simple description of the diagram] Figure 1 is a schematic diagram of a pump lift example that can operate a pump rod string in a subterranean formation; Figure 2 is a slight decomposition of the pump lift system shown in Figure 1: Figure 3 A more detailed longitudinal section view of one of the cylinder assemblies Fig. 3A is a detailed end view of the cylinder head shown in Fig. 3; the impact is removed to remove the cylinder 22. Sexuality, which is raised, the procedures of the cavities; in order to prepare the system to be able to be implemented by the implementation of the sacred 130 and the real ε body map; -19- 200813316 4th figure is the 3rd figure Another *longitudinal section of the main component of the non-cylinder assembly, and the cylinder assembly is in the state of completing the upstroke or in the raised position; Figure 5 is the cylinder shown in Figures 3 and 4. Another longitudinal section of the assembly, the cylinder assembly is in the state of completing its downward stroke; Figure 6 is a schematic view of the pump lift system shown in Figures 1 and 2, showing the hydraulic control circuit and Balancing the gas supply to the cylinders; Figure 7 is a longitudinal cross-sectional view of another embodiment of a cylinder assembly using only nitrogen as the balancing fluid, and the cylinder assembly is shown to be in an elevated position; a longitudinal sectional view of the cylinder assembly shown in Fig. 7, and the cylinder assembly is shown in a state in which the downstroke is completed; Fig. 9 is a schematic view of the pump lift system shown in Figs. 1 and 2, The pump lift system is equipped with a modified type of hydraulic circuit and nitrogen source; a detailed longitudinal cross-sectional view of the retarder cylinder for the hydraulic circuit shown in FIG. 9, and the retarder cylinder is provided with a piston head that is at the beginning of a rising stroke and is located at the end of the moving end; and FIG. It is a longitudinal sectional view of the retardation cylinder shown in Fig. 10, and the retarding cylinder is at the beginning of a descending stroke and is located at the end of the opposite moving end. [Main component symbol description] 10 Chest lift system 12 Base frame / platform 14 Adjusting screw 16 Concrete base 18 Chestnut/suction rod -20- 200813316 18 Pump rod string / suction rod string 20 Casing 22 Cylinder assembly 22 ' Cylinder assembly 24 Piston 25 Limit switch 26 Crossbar 30 Hydraulic motor / Pump 32 Sump 34 Nitrogen supply / Supply tank 36 Control panel 38 Pump rod pin 40 I-beam 42 Lateral bracket 44 Cylinder sleeve retainer 46 Connecting plate 48 U-bolt / connecting strap 50 Conical head 50' Piston head 52 Upper beveled edge 54 Tubular receiving member 56 Inner tapered wall 60 Piston shaft 61 Upper threaded end 62 Piston tube - 21 - 200813316 63 Lower 64 Live 66 dense 66, dense 68 grind 72 lower 73 inner 74 inner 75 cylinder 76 elbow 77 78th liquid 79 connect 80 80, rm 82 outer 83 end 84 round 85 row 86 school 87 lower 88 outer 90 outer 92 inner 92, cavity end / hole Plug/piston end seal seals consumption ring thread end concentric passage wall/sleeve head fittings two fittings pressure tube □ domain/outer chamber field concentric cylinder plate cylindrical extension plugging quasi-ring thread end/ Ring base Shoulder chamber/channel chamber/fluid channel-22- 200813316 96 Upper λ mountain m part 100 cylinder head 101 discharge hole 102 piston tube 103 upper internal thread 丄山 m part 104 inner seal 104' inner seal 106 sleeve 107 Oil seal 107' oil seal 108 connection □ 109 I 祖 33⁄4 fluid passage 110 connection □ 110' connection □ 111 line 1 12 directional control valve 1 13 valve slide shaft / valve 1 14 ascending line 115 line 116 flow control valve 118 lower return line 120 Pressure relief valve 122 shut-off valve 123 into □ line 124 out □ line -23- 200813316 / 126 remote control switch 130 delay cylinder 132 outer cylindrical tube 134 end plate 135 fastener 136 sealing plate 137 ◦ ring 142 air vent 144 Piston head 146 oil seal 148 wear ring G gas F, oil F oil-24-